Control system



P. S. DICKEY CONTROL SYSTEM Aug. 22, 1939.

original Filed Dec. 18, 1935 5 sheets-sheet 1 INVENTOR PAUL D/c/ffy ATTO EY Aug. 22, 1939.

P. S. DICKEY CONTROL SYSTEM Original Filed Dec. 18, 1935y 5 Sheets-Sheet 2 Aug. 22,1939.

P. S. DICKEY CONTROL SYSTEM original Filed Dec. 18, 1935 5 sheets-sheet :5

INVENTOR.

PA UL S. D/c/fy /fV/m my( Af.

' ATTORNEY,

Eaton@ @kk QQINQIN NGN w .QQ

P. S. DICKEY CONTROL SYSTEM Aug. 22, 1939.

Original Filed Dec. 18, 1935 5 Sheets-Sheet 4V Aug. 22, 1939. P. s. DlcKEY 2,170,347

' boNTRoL SYSTEM o riginal'Filed Dec. 18, 1955 5 sheets-sheet 5 Patented Aug. 22, 1939 CONTROL SYSTEM Paul S. DickeyrCleveland, Ohio, assignor to Bailey Meter Company, aY corporation oi Delaware Application 17 Claims.

This invention relates `to a method and means i'or Operating and controlling the operation of vapor generators; particularly vapor generators of the drumless, forced ow type, having a fluid 5 ow path including one or more long small-bore tubes, in which the ow in the path is initiated by the entrance of liquid under pressure at one end, and the exit of vapor only at the other end; characterized by an inflow of liquid normally D greater than the outflow of vapor, the difference being diverted from the path intermediate the ends thereof.

Such a vapor generator having small liquid storage and operated with wide range combustion de- 5 vices forms a combination rendering practical extremely high heat release rates with the consequent ability to economically handle practically instantaneous load changes from minimum to maximum, and vice versa, without heavy stand- 20 by expense, and is particularly suitable for operating conditions such as locomotive service,

, where load variations are of a wide range and arel required to be met substantially instantaneous y.

' capacity with a maximum heat absorbing sur-'- face so disposed and arrangedvas tobesubstan-f tially instantaneously responsiveto rapid changes and wide diversities in heat releasev rate yin the 30 furnace. The heat absorbingsurface is arranged 3; tinuously increasing -r'esistance"7'tojv gas flow throughout the lengthof the passage.:

the working medium, is comprised of one or more long small-bore tubes with anenlargement, preferably at the end of the generating section, which acts as a separator to divide liquid and vapor. The vapor is then passed through a superheater, while the excess liquid carried through the tubes for the purpose oi wetness and preventing scale o deposit, is diverted out of theseparator under regulated conditions, as will be hereinafter set forth. From the separator there is a normal continuous and an additional regulated spillover of diversion of a part of the liquid entering the economizer under pressure, sothat there is always being fed to and through the leconomizer and vapor generating sections more liquid than can be converted into vapor in a single passage therethrough, although the proportion of such excess 'I'he .generator has a minimum liquid storage yand ywide variations' inA rating.- v

ystudy of the specification 'and which: in relation to the path of the products oi com-.1 bustion and radiantheating. sothat thev entering f liquid is received at the c oolerend'of-the path; n Further,.the vapor-'generatOrinsofar as the sage of combustion gases isconcerned hasl a con-1V December 18, 1935, Serial No. 55,024

Renewed March 4, 1939.

liquid represents but a small part of the total volume of uid passing through the vapor generator and is at most times only sufficient to insure tube wetness and to carry off scale forming material.

In vapor generators of the character mentioned having small liquid and heat storage with high heat release capabilities, the liquid inflow must of necessity be continuous and at all times lproportioned to the vapor outflow, at the same time taking into account the desired diversion of excess liquid from the flow path. Furthermore to accomplish the wide range in heat release with substantially instantaneous response and to perform the combustion process efficiently, a method and means for operating such a vapor generator in accordance with varying conditions must be provided.

A principal object of the invention is to so control the operation of such a Vapor generator 0 as to satisfactorily produce wide changes in heat release rate with great speed, through proper regulation of liquid inflow and of the elements of combustion.

-, V.A further Objectis to maintain the efficiency of 5 ,combustion uniformlyv high, regardless of sudden ther objects will become evident from a of the drawings, in

Fig. 1 diagrannnatically illustrates a drumless forced iiow vapor generator to which the present l invention'. is'directed.

Fig. 2' diagrammatically illustrates a drumless lfo'rced'flow vapor generator, combined with the. q requisite apparatus 'to control the functioning l thereof, and such apparatus shown in partially The heat absorbing surface, or flow path vfor;-

diagrammatic fashion.

3 is in general similar to Fig. 2 but comprising different apparatus for performing'the method. y

Fig. 4 is a 'sectional elevation of a pilot valve.

Fig. 5 is a sectional elevation of a pneumatic relay.

Fig. 6 is similar to Fig. 5 but embodies certain additional features of construction.

Figs. 7 and 8 are wiring details relating to Fig. 3.

Fig. 9 is a sectional elevation of an operating `mechanism of Fig. 3.

In the various drawings, identical parts bear '50 the same reference numerals.

The drumless forced flow vapor generator to which the present invention is directed is diagrammatically illustrated in Fig. 1 to indicate 55 surface arranged as contained within the enclosure represented by the dot and dash lines.

The flow path for the working medium is comprised of long small-bore tubes'brought together at suitable headers. The generator includes an economizer 202 at the cooler end of the gas passage and which receives liquid from a. positive displacement pump as shown connected to the hot., Well.

The liquid from the economizer outlet header 20| is conveyed by a tube 203 to a manifold tube 204 from which the liquid is distributed to the generating section through in this instance, five fluid flow resistors 205, each of which has a greater resistance vdrop than the particular fluid flow passage which it serves and whereby the liquid is proportionately distributed to each of the tubular fluid flow passages 206,. 201, 208, 209 and 2I0 constituting the generating section of the assembly, which comprises floor, wall, screen and roof portions as indicated.

These five flow circuits comprising the vapor generating surface tangentially enter a bulge in the fluid flow path which is in the form of a separating chamber 232 for dividing the fluid into liquid and vapor; the vapor passing to a superheater 242, and the excess liquid being diverted from the uid ow path to a pipe I to the hot well or to waste. A normal continuous spillover occurs through the restriction 2 while a variable spillover occurs through the regulating valve 3.

The "heat source" (Fig. 1) includes a pulverized i fuel burner 4 supplied by a pipe 5 (Fig. 2) and an air chamber 6 supplied by a secondary air conduit 1. In order to provide for initial ignition of the pulverized fuel firing means, a gas-firing device 8 is supplied by a pipe 9 with a ow of gas under the control of a solenoid actuated valve I0. Referring now in particular to Fig. 2, I illustrate the fluid flow path ,as a single sinuous tube, to the'economizer section 202 of which, liquid is supplied under pressure to a pipe I I from a pump 289, which while it is illustrated in Fig. 1 as a positive displacement pump may be of any suitable type, and which I have therefore illustrated in Fig. 2 merely diagrammatically. From the economizer section the uid passes to and through the generating section discharging into the separator 232. From the separator, vapor passes to and through the superheater 242, leaving by the conduit 244 to a main turbine I2 illustrative of a vapor consuming device. Products of combustion pass successively through the generating section, surheater, and economizer and may contact a part or all of the separator.

An auxiliary turbine 281 drives a liquid feed pump 289, the secondary air blower I3, the primary air blower I4, the pulverizing mill I5, and a fuel feeder I6, the latter under the control of a variable speed driver II. While I have illustrated these devices diagrammatically and as though all are located to be driven by the same shaft and at the same speed, it will beunderstood that the necessary gear reduction, or driving connections between the several devices, are known and would be properly designed as to relative speed, power, etc., and that I merely intend to indicate that the auxiliary turbine 281 drives these devices simultaneously and in unison.

The rate of supply of pulverized fuel to the burner 3 is primarily controlled by the speed of the pulverizer I5, but is further regulated by the rate of feed of raw coal to be pulverized, going to the pulverizer I5 from the feeder I3. Variation in such rate of feed of raw coal is under the control of the variable speed device I1. The supply of fuel to the furnace is further influenced by the amount of primary air sweeping through the pulverizer I5 and this is in turn a function of the relative position of the damper I8 at the outlet of the secondary air blower and the position of the damper I9 in the secondary air conduit 1.

The rate of supply of air to support combustion is primarily determined by the speed of the secondary blower I3 and of the primary blower I4, but is further influenced by the position of the damper I8. The total air supplied for combustion is proportioned through the conduits 5 and 1, dependent upon the relative positions ofthe dampers I8 and I9. It Will be noted that the air from the secondary blower I3 passes to the air heater 20 from where it divides, a part going as primary air to and Athrough the primary blower I4 and the remainder under the control of the damper I9 going through the conduit 1 Ato the of the elements of combustion to the heating furnace.

I indicate at 23 a pressure responsive device such as a Bourdon tube connected to the conduit 244 and having an indicator pointer 24 adapted to cooperate with an index 25 for advising the instantaneous value of the vapor outflow pressure.

As an indicator of generator output,.,or load upon the vapor generator, I provide a Bourdon tube 26 adapted to position an indicator pointer 21' relative to an index 28. The Bourdon tube 26 is connected by means of a, capillary with the turbine I2 at a location such that the Bourdon tube will be sensitive to first stage shell pressure of the turbine, which pressure bears a substantially straight line relation to rate of steam flow. Thus the pointer 21 will indicate, relative to the scale 28, a reading representative of rate of flow of steam from the vapor generator and therefore an indication of output or load upon the generator.

29 represents means responsive to liquid level Within the separator 232 and constitutes a pressure casing enclosing a mercury U-tube connected across the vertical elevation of the separator. A float is adapted to rise and fall with the surface of the mercury in one leg and to thus cause a positioning of a pointer 30 relative to an index 3| to advise the instantaneous value of liquid level within the separator.

A ilow meter 32 is adapted to position an indicator 33 relative to an index 34 to advise the instantaneous value of the rate of Vapor outflow from the vapor generator. A rate of flow meter 35 positions an indicator 36 relative to an index 31 to provide an indication of the rate of flow of air for combustion leavingfthe secondary air blower I3.

The ow meters 32 and 35 are of a known type such as is disclosed in the patent to Ledoux, No. 1,064,748. Such a meter is a differential pressure responsive device adapted to correct for non-linear relation between diierential pressure and rate of flow, to the end that angular posithe flow meters the outline of the internal construction wherein is a liquid sealed bell having walls of material thickness and shaped as described and claimed in the above mentioned Ledoux patent.

I preferably primarily control the supply of liquid to the fluid flow path and the elements of combustion to the furnace, through variation in speed of the auxiliary turbine, utilizing the liquid inflow as the basis for such control. Realizing, however, the possible diiference in characteristics of the pumps and blowers, as well as variations in conditions of operation, I provide readjusting means to supplement the primary control of the elements of combustion. For the air, such readjusting means comprises the damper I8 positioned at the outlet of the secondary air yblower I3 by a pneumatic actuator 38. Also the damper I9 positioned in the conduit 1 by a pneumatic actuator 39. For the fuel the readjusting means comprises the variable speed driver I1 and its effect upon the raw coal feeder I6.

The speed of the auxiliary turbine is regulated through varying the opening of governor valves admitting steam to the turbine. Such steam for example may below pressure steam from the exhaust of the main turbine I2 or extraction steam' therefrom, or it may be high pressure steam direct from the vapor generator. A

pneumatic actuator 4II positions the governor valves under the influence of an air loading pressure established by a standardizing relay 4I illustrated in detail at Fig. 6.

In order to regulate the liquid inflow (through variation in speed of the liquid pump) I preferably accomplish the regulation responsive to liquid inflow, vapor outflow, and level of liquid in the separator.

As previously mentioned, the Bourdony tube 26 is positioned responsive to turbine shell pressure representative of vapor outflow from thev vapor generator and is adapted to vertically position a pilot stem 42 relative to a pilot casing 43, to which ya supply of compressed air may be available as indicated by the small arrow. Such a pilot valve is shown in detail at Fig. 4 and forms the subject matter of a patent to Clarence Johnson No. 2,054,464. y l

Air under .pressure is supplied to the interior of the casing 43 intermediate the pilot lands 44, which lands are so spaced along the stem 42 as to coincide with narrow annular ports` 45. When the-pilot stem is axially moved in the casing so that the lands 44 are moved relative to the ports 45, then a denite loading pressure is available in the annular ports bearing a known relation to the amount of such movement. For example, if the stem 42 is moved upwardly there is available at the upper left-hand exit of the casing 43 a loading pressure increasing in definite relation to such movement, while if the stem 42 is moved downwardly there is available at the lower lefthand exit a pressure increasing definitely with such movement.

I indicate pipes or capillaries for transmitting such air loading pressures, throughout the drawings, by dotted lines to distinguish from electrical connections, or other pipes or conduits. In Fig. 2

then, such a connection is illustrated at 46 for transmitting an air loading pressure bearing a 'known relation to rate of vapor outflow to a differential relay device 41. Such a diierential relay is illustrated in detail at Fig. 5.

In similar manner the liquid level indicator 23 vertically positions a pilot stem 48 to establish at the relay 41, through the connection 48, an air loading pressure representative of liquid level.

Y Referring to Fig. 5 the connection 46 leads to a chamber 50, separated by a diaphragm or movable partition 52 from a chamber 5I open to the atmosphere. The diaphragm 52 and loading spring 53 are both connected to a stem` 54 to which is also attached a diaphragm 55, separating the chambers 56, 51. Connection 43 leads to the chamber 56. A supply of air under pressure is available through the connection 58 to the chamber 51 under the control of a valve 59. Exhaust from the chamber 51 to the atmosphere is under the control of a valve 60. The stem 54 is adapted to position a valve actuator 6I to either admit air under pressure through the valve 59, thus increasing the pressure within the chamber 51, or to bleed air to the atmosphere through the valve 60 and thus decrease the pressure within the chamber 51. Pressure within the chamber 51 is transmitted through a connection 62 to a spring loaded diaphragm actuator for positioning the valve 2| in the suction line to the liquid pump.`

Certain features of the diiferential relay 41 are disclosed and claimed in my patent, 2,098,- 913.

It will be observed that variations in the loading pressure eiective through the connection 46, or that effective through the connection 48, will be effective to vary the air pressure within the chamber 51 and correspondingly effective upon the positioning of the valve 2I.

The valve 2I acts as a variable orifice across which there will exist .a pressure differential bearing a known relation to the rate of flow of liquid through the valve 2I. Pressures on opposite sides of the valve are effective through the pipes 63, 64 respectively in chambers 65, 66 of the standardizing relay 4I.

Referring now to Fig. 6 it `will be observed that the standardizing relay 4I is toa certain extent similar to the relay 41, with the additionv of a controllable bleed connection 61 between the chambers 56' and 51', certain features of which constructionare disclosed and claimed in the patent to Harvard H. Gorrie, No. 2,098,914. A loading pressure established within chamber 51 is effective through a connection 68 upon the pneumatic actuator 40 for positioning the turbine governing valves. In this instance the function of the controllable bleed connection 61 is to supplement the primary controlof the pressure effective upon the actuator 40 with a secondary control, of the same or different magnitude, as a follow-up or supplemental action to prevent over-travel and hunting, and wherein the positioning of the actuator 4I! will not necessarily be directly with the positioning yof the valve 2i. V L

In general the valve 2I is positioned responsive to vapor outflow and to liquid level within the separator and forms a variable orifice in the y suction line to the water pump. The device 4I receiving the diierential pressure lacross the valve 2| positions the actuator 40 and the turbine governing valves to control the speed of the Water pump in such manner that the differential pressure across the valve 2I will be held constant regardless of the opening of valve 2l and thus the liquid flow to the water pump is controlled proportional both to vapor outflow and to liquid level within the separator.

If vapor outflow increases, then the pilot stem 42 is raised proportionally, thus proportionally increasing the loading pressure effective through the connection 46, (torelay 41) causing a downward ,movement of the stem 54 and a corresponding opening of the valve 59 to additionally admit. air under pressure within .the chamber 51, thus increasing Athe air loading pressure the vapor generator.

It will then be observed that the valve 2I is positioned responsive to vapor outiiow from the generator and to liquid level in the separator, while the speed of the water pump is not only responsive to these two variables but additionally to the rate of iiow of water to and through the pump.

The liquid level responsive device 29 further controls, through the pilot stem 46, the positioning of the variable spillover valve 3 in such manner that upon a rise in liquid level within the separator 232 above a predetermined elevation there will be a regulated opening of the valve 3 to supplement the normal spillover 2 to the pipe I.

Certain features of the control through the utilization of turbine shell pressure are disclosed and claimed in the co-pending application of Ralph `M. Hardgrove, Serial No. 55,027, filed of even date herewith. Certain features directed to the control of the auxiliary turbine are disclosed and claimed in my co-pending application, Serial No. 55,026, filed of even date herewith. Certain features relating to multiple and sequential control from liquid-level within the separator are disclosed and claimed in the co-pending joint application of Ervin G. Bailey and Paul S. Dickey, Serial No. 55,025, led of even date herewith.

Under the control of vapor outflow pressure acting upon the Bourdon tube 23, I provide a pilot valve 69 for establishing an air loading pressure through the connection to position the by-pass valve 22 and the damper I8. Upon a fall in vapor pressure from predetermined value the valve 22 and the damper I8 both tend to open, each from a predetermined position. This action is particularly desirable upon sudden material increases in load upon the unit as a whole, thus causing a marked decrease in vapor pressure. When such sudden and material increases in vapor outflow occur, thereby lowering the vapor pressure, the auxiliary turbine speed is increased and the damper I8 is opened. At

such time it may be that momentarily the increase in speed of the water pump and correspondingly the liquid inflow to the vapor generator would be increased more than would be desired to utilize the available heat storage .of the unit, 'and during such short intervals of time it is desired that a portion of the water pumped be 'by-passed from the outlet to the inlet side of the pump. The adjustment of the actuator 38 and of the actuator of the valve 22 is preferably such that they will be responsive only to predetermined variations in vapor pressure and correspondingly air loading pressure in the connection 16. For example, the damper I8 may be regulated as to position upon any departure of vapor pressure from predetermined value in either direction, while ,the valve 22 may be completely closed until vapor pressure` has fallen a predetermined amount below the desired standard. Beyond that point the valve 22 would begin to. open and the damper I8 may, or may not,

be completely open while the opening of the valve 22 is being regulated.

I preferably primarilycontrol the supply of the elements of combustion through varying the speed of the auxiliary turbine and thereby in unison with the rate of liquid inflow. I readjust i the total supply of air to support combustion by the positioning of the damper I8 at the outlet of the secondary air blower responsive to variations in vapor outflow pressure.

I then proportion the air supplied through the conduit 1 to the vapor outfiow from the generator. I accomplish this through the interaction of flow metersl 32, which co-act to position a pilot stem 1I for establishing an air loading pressure to which the actuator 39 is responsive.

The speed of the raW coal feeder I6 is con-v trolled through lthe variable speed drive I1 from an electric contactor device 12. Herein is the means for increasing or decreasing thev rateof verized fuel through certain sections of the pulverizer. I

The pressures acting upon the diaphragm 15 are proportional to the resistance drop through Vthe pulverizer and are affected not only by the quantity of air flow through the orifice 16, and correspondingly through the pulverizer, but also influenced by the amount of unpulverized or partially pulverized fuel within the pulverizer. Thus if the rate of feed of raw coal to the pulverizer is greater than desired the amount of raw or partially pulverized fuel in the pulverizer will build up, thus Varying the pressure drop across the pulverizer effective upon the diaphragm 15,

'which in turn actuates the contactor arm 13 to be effective upon the variable speed driver I1 to slow down the raw coal feeder I6. Conversely should the pressure drop effective'upon the diaphragm 415 be less than desired relative to the pressure drop effective upon the diaphragm 14, then the contactor arm 13 will cause an increase in the rate of supply of raw coal through the feeder I6.

In Fig. 3 I illustrate an embodiment of my invention wherein I utilize electric means for carrying out the method, rather than the air actuated apparatus which I have described in connection withFig. 2.

The Bourdon tube 26 positions a variable area electrode of an electron discharge device 11 for controlling the positioning of an actuator 18 at the valve 2|. In the drawings a single line 19 connects the device 11 with a relay panel 80 which is in turn connected by the conductor 8| with the actuator 18 and by the conductor 82 with the device 83. The latter is connected by a conductor 84 with a relay'panel 85. The device 83 is similar to the device 11 and is controlled by the water level responsive device 29A. From the relay panel 85 a conductor 86 joins the actuator of the valve 3.

A pressure differential responsive device 81 is effective in positioning the movable element of an electron discharge device 88 connected to a relay panel 89 and from there lconnected with the actuator 40A. The ratio meter 90' combines the functions of the meters 32,35 of Fig. 2 to compare the rate of vapor outflow and the -rate of air flow through the conduit 1, and upon departure from predetermined relation between the two is adapted to move 'the movable electrode of an electron discharge device 9| connected to a relay panel 92 and to the actuator of the damper I9.

'I'he conductors indicated at 19, 8|, 82, 84, 86, etc., are meant to be cables which may have one or more wires, but the cables are shown as a y single line to simplify the drawings.

'I'he Bourdon tube 23 positions the movable electrode of an electron discharge device 93 which is connected through the relay panel 94 to the actuators 95 and 96.

Referring now'to Fig. 7 I show the .detailed wiring of a relay panel such as 85, 89, 92 and 94. Taking the panel 85 as representative, and referringto Fig. 7, it will be observed that the arm 91, positioned by the water level device 29A, is

adapted to move the anode of the electron discharge device 83 relative to the cathode. In connection with the construction of said electron discharge device reference is made to the co-pending application of Elmer D. McArthur, Serial No. 23,- 194, flied May 24, 1935, and. in connection with certain circuits including such a device reference is made to the patent to John' D. Ryder No. 2,112,682. y

The cathode of the device 83 is connected to the secondary of a heating transformer 98. .99 and |00 are resistances, |0| is an inductance, |02 a transformer, |03k an electron discharge device, and |04 a motor. 'Ihe general purpose of the electron discharge device* |03 is to control a flow of pulsating direct-current for speed control of the motor |04, whichrotates in a -single direction fromlzero to maximum speed dependent upon the current passage of the device |03.

, The control of such current passage is through controlling the percentage of time of which the device |03 is allowed to conduct, and this by impressing upon the grid of the device |03 the sum of an AC and DC voltage. The AC voltage lagging in phase with respect to the plate voltage through the action of a phase shifting bridge |00, |0|, |02 and therefore the point in the cycle at which the grid voltagelreaches the threshold value, and allows the device |03 to conduct, may be varied by varying the magnitude of the DC voltage which is in series with the AC voltage. Such variation in magnitudeof the DC voltage -is accomplished through varying the effective area of the anode of the device 83by mechanically moving the arm 91. Thus the speed of rotation ofthe motor |04, forming a part 0f the actuator |05, is varied through the positioning of the arm 91 by the level responsive device 29A.

Fig. 8 illustrates the arrangement of relay panel 80.in,connection with the electron discharge devices 83 and 11 which are connected in parallel 'to control -the motor |08 of the actuator 18 jointly in response to vapor outflow and liquid level.'

At Fig. 9 I illustrate a vertical elevation partially sectioned of the actuator |05, which is typical of the actuators 18, 95, 96, 40A, |05, etc. of Fig. 3. 'I'he motor |04 is the nlotor of the same number of Fig. 7 and is adapted to rotate in a single direction from zero to a minimum speed and at a speed varying with the current impressed across its armature,'as clearly indicated in 7 and 8.

Rotation of the armature drives a uid pump |01 forcing a fluid such as oil from the chamber |08, above the piston including the pump |01, to the chamber |09below the piston. Such a transfer of fluid from one side ofthe piston to the other tends to move the piston upwardly and such motion is opposed by a compression spring in a manner clearly indicated. I'he pressure which is opposed by the spring varies with the speed of the motor |04 and if one end of thedevice, for example as at 0, is pivotally supported in a relatively fixed manner, then a change in the speed of the motor |04 results in a movement of the end relatively toward or away from the end I I0 and such movement, if applied to a valve or other device to be positioned, results in a positioning of such device.

It wlll,of course, be observed that by changing the direction of rotation of the pump |04 the spring opposing motion may be in tension rather than in compression. Furthermore such spring loading may be external of the ,device rather than internal.

While I have chosen to illustrate and describe certain preferred embodiments of my invention, it is to be understood that this is by way of illustration Yonly and that I am not to be limited thereby except as to the claims in view of prior art.

.What I claim as new, and desire to secure by Letters Patent of the United States, is:

the steps of, controlling liquid inflow and the supply of fuel and air for combustion in accordance with load on the generator, readjusting air supplied from vapor outflow pressure, and further controlling the air supplied to maintain predetermined vapor outow-air flow relation.

2. The method of operating a vapor generator of the drumless forced flow type, which includes the steps of, controlling liquid inflow and the supply of fuel andair for combustion in accordv'ance with load on the generator, readjusting air supplied in accordance with vapor outflow pressure, and proportiofning the air in two streamsv to the furnace in accordance with rate of vapor outflow and rate of total air flow.-

3. The method of operating a vapor generator of the drumless forced flow type, which includes the steps of, controlling the supply of pulverized fuel and air for combustion in accordance with load onthe vapor generator, readjusting total air supply from vapor outflow pressure, and dividing total air supply into a primary air stream and a.. secondary air stream, such division responsive to vapor outflow-total air flow relation.

4. An auxiliary power unit for a vapor generator, comprising in combination, a liquid supply pump, a secondary air blower, a primary air blower, a fuel pulverizer, a raw fuel feeder to Figs.

the pulverizer, and a. power means adapted to drive all of said devices in unison and responsive to a variable'in the operation of the vapor generator.

5. In combination, a vapor generator, a pulverizer for supplying pulverized fuel to the furnace of the vapor generator, an air blower for supplying air to support combustion of the pulverized fuel, a regulator for controlling the pulveriZer and blower and responsivey to a variable in the operation of the vapor generator, means for dividingthe air supply to provide a primary air stream to act as a carrier for pulverized fuel, and means responsive to vapor outflow and to total air flow for controlling said last named means. y

6. In combination, a vapor generator having fuel supply means and air supply means, a meter of the vapor outflow, a meter of the air supplied, said meters coacting to establish an air loading pressure representative of vapor outilow-air ilow relation, and meansdividing said total air supply into two streams and controlled by said air loading pressure.

'7. In combination, a vapor generator of .the drumless forced flow type having a separator between the generating` and superheating portions of the fluid flow path, a liquidsupply pump, an air supply blower, and a fuel pulverizer; power means for driving said pump, blower, and pulverizer in unison; and regulating means for said power means responsive to variations in liquid level in said separator.

8. 'I'he combination with a vapor generator of the drumless forced flow type receiving liquid under pressure at one end and delivering superheated vapor at the other, means controlling liquid inflow and the supply of fuel and air for combustion responsive to an indication of load on the generator, means readjusting air supply responsive to an indication of vapor outflow pressure, and further means readjusting air supply to maintain predetermined vapor outflow-air flow relation.

9. In combination, a vapor generator of the drumless forced flow type having a separator between the generating and superheating portions of the fluid flo-w path, a turbine adapted to operate liquid and fuel and air supplying means for the vapor generator in unison, a regulating valve in the liquid supply line, means jointly responsivev to an indication of generator load and to liquid level in the separator for positioning said valve, means sensitive to pressure differential across said valve, and speed governing mechanism for the turbine under the control of said last named means.

10. The combination with a vapor generator, of a liquid supply pump, an air supply blower, and a fuel supply means; power means for driving said pump, blower, and fuel supply means in unison and responsive to a variable in the operation of the vapor generator; a by-pass around the liquid supply pump, and means responsive to a variable condition of the vapor generated adapted to simultaneusly control the opening of said by-pass and to regulate total air supply.

11. 'Ihe combination with a vapor generator, of a liquid supply pump, an air supply blower, and a fuel supply means; power means for driving said pump, blower, and fuel supply means in unison and responsive to a variable in the operation of the vapor generator; a by-pass around the liquid supply pump, and means responsive to vapor outflow pressure adapted to simultaneously control the opening of said by-pass and to regulate total air supply.

12. 'Ihe combination with a vapor generator, of a liquid supply pump, an `air supply blower, and a .fuel supply means; power means for driving said pump, blower, and fuel supply means in unison and responsive to a variable in the operation of the vapor generator; a by-pass around the liquid supply pump, means responsive to a variable condition of the vapor generated adapted to simultaneously control the opening of said bypass and to regulate total air supply, and means dividing the total air supplied into two streams responsive to vapor outflow-air flow relation.

13. The combination with a vapor generator, of a liquid supply pump, an air supply blower, and a fuel supply means; power means for driving said pump, blower, and fuel supply means in unison and responsive to a variable in the operation of the vapor generator; a by-pass around the liquid supply pump, and means responsive to vapor outflow pressure adapted to simultaneously control the opening of said by-pass and to regulate total air supply, and means dividing the total air supplied into two streams'responsive to vapor outflow-air flow relation.

14. An auxiliary power unit for a vapor generator, comprising in combination, a liquid supply pump, a secondary air blower, an air blower for primary air for supplying fuel to the generatori" fuel preparation and supply means, and a power means adapted to drive all of said devices in unison and responsive to a variable in the-operation of the vapor generator.

15. An auxiliary power unit for a vapor gener' ator, comprising in combination, a liquid supply pump, a secondary air blower, an air blower for primary air for supplying fuel to the generator, solid fuel supply means, and a power means adapted to drive all of said devices in unison and responsive to a variable in the operation of the vapor generator.

16. In combination, a vapor generator having fuel supply means and air supply means, a meter of the vapor outflow a meter of the air supply, said meters coacting to establish an air loading pressure representative of vapor outflow-air flow relation, and means dividing said total air supply into a plurality of streams and controlled by Said air loading pressure.

17. In combination, a vapor generator of the drumless forced flow type having a separator between the generating andsuperheating portions of the fluid flow. path, a turbine adapted to operate liquid and fuel and air supplying means for the vapor generator in unison, an adjustable orifice in the liquid supply line, means jointly responsive to an indication of generator load and to liquid level in the separator for positioning said orifice, means sensitivev to pressure differential across said orifice, and speed governing mechanism for the turbine under the control of said last named means.`

' PAUL S. DICKEY. 

